EP3074335B1 - Entraînement de main courante pour un escalier ou un trottoir roulant - Google Patents

Entraînement de main courante pour un escalier ou un trottoir roulant Download PDF

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Publication number
EP3074335B1
EP3074335B1 EP14799744.9A EP14799744A EP3074335B1 EP 3074335 B1 EP3074335 B1 EP 3074335B1 EP 14799744 A EP14799744 A EP 14799744A EP 3074335 B1 EP3074335 B1 EP 3074335B1
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EP
European Patent Office
Prior art keywords
drive
handrail
counterpressure
tension spring
counter
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP14799744.9A
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German (de)
English (en)
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EP3074335A1 (fr
Inventor
Csaba BOROS
Michael Matheisl
Wolfgang Neszmerak
Robert Schulz
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Inventio AG
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Inventio AG
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Priority to EP14799744.9A priority Critical patent/EP3074335B1/fr
Publication of EP3074335A1 publication Critical patent/EP3074335A1/fr
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Publication of EP3074335B1 publication Critical patent/EP3074335B1/fr
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66B—ELEVATORS; ESCALATORS OR MOVING WALKWAYS
    • B66B23/00—Component parts of escalators or moving walkways
    • B66B23/02—Driving gear
    • B66B23/04—Driving gear for handrails
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66B—ELEVATORS; ESCALATORS OR MOVING WALKWAYS
    • B66B23/00—Component parts of escalators or moving walkways
    • B66B23/16—Means allowing tensioning of the endless member
    • B66B23/20—Means allowing tensioning of the endless member for handrails
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66B—ELEVATORS; ESCALATORS OR MOVING WALKWAYS
    • B66B23/00—Component parts of escalators or moving walkways
    • B66B23/22—Balustrades
    • B66B23/24—Handrails

Definitions

  • the invention relates to a conveyor system which is designed as an escalator or moving walk and a handrail drive for such a conveyor system.
  • the known handrail drive has a drive device and a pressure device. Between the drive device and the printing device, a handrail is guided, wherein the top of the handrail pressure rollers facing the printing unit. The upper side is that side of the handrail on which the users of the escalator lay their hand to hold on to the handrail.
  • the drive means on rollers which are assigned to a part of the pressure rollers, wherein between the rollers of the drive means and the handrail, a drive belt runs.
  • the drive belt is also passed around a drive wheel and a tensioning wheel to tension the drive belt.
  • the pressure rollers press the handrail against the driven drive belt, the drive belt being supported by the rollers of the drive device.
  • the pressure force with which the pressure rollers act on the handrail is applied by a spring of the pressure device.
  • the side of the step band arranged handrail drive can also lead to deeper pits on site, so that the handrail drive, in particular the spring of the handrail drive, has sufficient space.
  • the object of the invention is to provide a handrail drive for driving a handrail of a transport system, which allows the use of the widest possible step band or pallet band at a given width of the conveyor system is optimized in terms of its height.
  • the handrail drive for driving a handrail of a conveyor system has at least one drive device and at least one counter-pressure device, wherein the counter-pressure device includes at least one tension spring and at least one counter-pressure roller.
  • the handrail is guided between the drive device and the at least one counter-pressure roller approximately in a linear direction and is acted upon by the at least one counter-pressure roller against the drive means with a pressure force caused by the tension spring.
  • the optimized height is achieved in that the tension spring is arranged approximately parallel to the direction that the at least one counter-pressure roller is at least partially disposed in an extension of the tension spring and that the handrail drive has a mechanical deflection, by means of which the spring force of the tension spring in the pressing force the at least one counter-pressure roller is deflected.
  • the drive device has at least one driven drive belt.
  • the drive belt and the at least one counter-pressure roller are arranged to each other that the handrail between the drive belt and the at least one counter-pressure roller can be guided and by the at least one counter-pressure roller against the drive belt with the pressing force can be acted upon.
  • the handrail of the conveyor system is not part of the handrail drive.
  • the handrail drive can also be manufactured and distributed independently of a handrail suitable for this purpose.
  • the handrail drive can also be suitable for differently configured handrails or optionally also be adaptable in the sense of a modular design for different applications, in particular different types of handrails.
  • transport systems that are designed as an escalator or moving walk.
  • a preferred use of the handrail drive is for moving walks, which are designed flat construction. This can be realized by the inventive design a moving walkway, which sits flat on the ground. The floor of a building, a covered feeder area or the like can then be designed just. This is to be understood that the floor does not need to be opened for installation of the conveyor system, since the handrail drive can be completely housed in the balustrade base.
  • a flat handrail drive is also very suitable for modernizing a conveyor system.
  • a new balustrade can be arranged with a handrail on the existing escalator or the existing moving walk without making extensive changes to existing components of the conveyor system, for example, on the truss, on the rails or on the rail blocks.
  • the ability to provide by means of the handrail drives according to the invention conveyors with smaller external width with the same stage or pallet bandwidth, the replacement of an existing, old conveyor system by a new conveyor system is much easier.
  • the ease of maintenance is improved, since the handrail drive according to the invention is very compact and can be mounted on the framework, instead of extending to the side of the framework.
  • the drive device may comprise at least one drive wheel, at least one tensioning wheel and a plurality of contact pressure rollers.
  • the drive belt is driven by the drive wheel and is arranged circumferentially between this and the tensioning wheel.
  • the contact pressure rollers are arranged inside the drive belt loop and support the drive belt against the handrail.
  • the counter-pressure device has a plurality of counter-pressure rollers. The counter-pressure rollers of the counter-pressure device on the one hand and the drive wheel, the tensioning wheel and the contact pressure rollers of the drive device on the other hand, are each assigned in pairs.
  • the drive wheel is opposed to one of the counter-pressure rollers, that the tensioning wheel is opposite to one of the counter-pressure rollers and that each of the contact pressure rollers is opposite to one of the counter-pressure rollers.
  • the driving force can be transmitted particularly advantageous to the handrail.
  • a slippage of the handrail is reliably avoided in this way.
  • the handrail can be guided in this way, at least largely without significant bending between the drive belt and the counter-pressure rollers in the direction.
  • not all rollers or wheels of the drive device is associated with one of the counter-pressure rollers.
  • the drive wheel and / or the tensioning wheel and / or one or more of the contact pressure rollers remain or remain without a directly associated counterpressure roller.
  • the drive wheel and the tensioning wheel can remain without a counter-pressure roller, wherein each of the contact pressure rollers of the pressing device is associated with one of the counter-pressure rollers of the counter-pressure device.
  • the counter-pressure rollers are arranged one behind the other in the extension of the tension spring.
  • the height required for the counter-pressure rollers can be optimized and used in an advantageous manner for accommodating the tension spring.
  • the counter-pressure device has a bearing body on which the counter-pressure roller is mounted or the counter-pressure rollers are mounted. It is also advantageous that a guide is provided which is at least indirectly connected to the drive device and that the bearing body is guided by means of the guide at least one point relative to the drive means at least approximately perpendicular to the direction. In this way, the position of the bearing body and thus each of the positions of the counter-pressure rollers in the running direction relative to the drive means, in particular the drive wheel and / or the tensioning wheel and / or the at least one contact pressure roller can be maintained, while in principle a movement play or a mobility or a degree of freedom is perpendicular to the direction of travel.
  • the pairwise assignment of the counter-pressure rollers of the counter-pressure device and the drive wheel, the tensioning wheel and the contact pressure rollers of the drive device can be ensured, wherein the distance between the counter-pressure rollers of the drive wheel, the tensioning wheel and the contact pressure rollers of the drive means is at least medium variable.
  • this movability of the counter-pressure rollers then acts, for example, in such a way that a necessary movement play can be achieved when carrying out the handrail. This can also be compensated if necessary provided on the handrail unevenness or adhering to the handrail contamination.
  • the mobility of the counter-pressure rollers makes it possible to set and maintain the desired pressure force caused by the tension spring.
  • the guide is rigidly connected to a tension spring bearing, on which the tension spring is supported, and that the spring force of the tension spring acts on the bearing body via the deflection device.
  • At least one first axis is provided fixedly on the bearing body, that the deflection device has at least one first axis guide, in which the first axis is guided, and that the axle guide the first axis with a predetermined deflection angle with respect to the direction of action the spring force of the tension spring leads.
  • predetermined deflection angle defines that, irrespective of the position of the axle within the axle guide, there is always a gradient in the axle guide which converts the spring force into the pressure force.
  • a first axis and at least one second axis are provided fixedly on the bearing body, that the deflection device has a first axis guide, in which the first axis is guided, and at least one second axis guide, in which guided the second axis , that the first axis guide guides the first axis with a predetermined deflection angle with respect to the direction of the spring force of the tension spring, and that the second axis guide guides the second axis with the (same) predetermined deflection angle with respect to the direction of the spring force of the tension spring , In this way, the spring force of the tension spring is deflected in their direction.
  • the magnitude implementation of the spring force of the tension spring results in ideal implementation, are neglected in the friction forces and the like, from the determined by the deflection angle parallelogram of forces.
  • the spring force of the tension spring can be translated depending on the deflection angle.
  • the deflection angle does not necessarily have to be constant over the length of the axle guide.
  • a progressive or degressive gear ratio between spring force and pressure force can be achieved.
  • damping the enabled by the tension spring vibration behavior can be used.
  • the friction in the at least one axle for vibration damping can be used. This friction can also be influenced by the choice of a corresponding deflection angle.
  • the deflection device has at least one Gleitmentsschuh that the counter-pressure device has a slideway and that the tension spring bearing on which the tension spring is supported, is arranged stationary to the slide. Further, the friction between the at least one Gleitmentsschuh and the slide can also be used to dampen the vibration system present by the tension spring.
  • the deflection angle which is provided in the axle guide or the axle guides, is preferably selected from a range of 10 ° to 45 °. Further, it is advantageous that the deflection angle is selected from a range of 10 ° to 30 °. It is also advantageous that the deflection angle is selected from a range of 15 ° to 25 ° and in particular about 20 °.
  • a counter-pressure roller is mounted on the first axis.
  • the counter-pressure roller, which is mounted on the first axis, is preferably the closest to the tension spring arranged counter-pressure roller. This embodiment also contributes to a compact construction of the handrail drive.
  • one of the counter-pressure rollers is mounted on the second axis. In the case of several counter-pressure rollers this means that one of the counter-pressure rollers is mounted on the second axle. If a plurality of counter-pressure rollers are provided, then it is advantageous that one of the counter-pressure rollers is mounted on the first axis and that one of the counter-pressure rollers is mounted on the second axis. In the case of several axes, which also includes the case of two axes, it is advantageous that in each case one of the counter-pressure rollers is mounted on each of the axes or at least on a part of the axes. This allows a space-saving design.
  • the counter-pressure roller which is mounted on the second axis, which is furthest away from the tension spring counter-pressure roller. If further axes, that is, more than two axes, are provided, then further counter-pressure rollers can be arranged in an advantageous manner between the first axis and the second axis.
  • a second axis is provided fixedly on the bearing body, that the deflection device has a second axis guide in which the second axis is guided and that the second axis guide the second axis with the predetermined deflection angle with respect to the direction of the spring force the tension spring leads.
  • Counter-pressure rollers may also be arranged on axles which are not guided in this way in the deflection device.
  • the conveyor system may have one or more handrail drives.
  • the individual handrail drive has due to the deflection on a direction dependent on the direction of contact pressure.
  • a suitable orientation for example, a higher pressure force can be achieved for the upward travel, while a lower pressure force is achieved for the downward movement.
  • the handrail can be spared during the descent.
  • the dependence of the (effective) pressure force of the running direction is caused by the fact that due to the deflection angle of the axle guide in the direction acting on the counter-pressure rollers forces counteract the force of the tension spring or add to this.
  • the larger the acute deflection angle the lower the influence of the direction of travel. In other words, the larger the deflection angle to be selected smaller than 90 °, the smaller the influence of the running direction.
  • the handrail drive can also have two counter-pressure devices, which are arranged mirror-symmetrically to a mirror plane. These two counter-pressure devices are only half as long as the drive device, so that one half of the required counter-pressure rollers of the first counter-pressure device are assigned and the other half of the required counter-pressure rollers of the second counter-pressure device are assigned.
  • the mirror plane extends orthogonal to the direction of travel of the handrail and is positioned approximately centrally of the drive means.
  • the conveyor system can of course also have several handrail drives.
  • two handrail drives can be used, which are oriented against each other. If the same pressure force is required in both directions, then the two handrail drives can be arranged mirror-symmetrically to each other.
  • Each handrail drive here has its own tension spring. In a modified embodiment, targeted direction of travel-dependent pressure forces can be adjusted in this way.
  • existing transport facilities can be modernized by: whose at least one existing handrail drive is replaced by at least one handrail drive according to the invention with a deflection device. If necessary, further changes to the existing conveyor system are necessary, for example, on the structure, on guides of the handrail, on electrical systems and the like.
  • FIG. 1 schematically shows a side view of a conveyor system 100, which is configured as escalator 100 and connects a first floor E1 with a second floor E2.
  • the escalator 100 has a supporting structure 106 or a framework 106 with two deflection regions 107, 108, between which a step belt 105 is guided circumferentially with a plurality of steps 104.
  • a handrail 3 is arranged circumferentially on a balustrade 102.
  • the balustrade 102 is connected at the lower end by means of a Balustradensockels 109 with the structure 106 or truss 106.
  • a handrail drive 2 is arranged in the interior of the balustrade pedestal 109.
  • the handrail drive 2 is fixed due to its low height to a top flange of the structure 106.
  • an escalator 100 has two balustrades 109, each with a handrail 3, the step belt 105 being arranged between the two balustrades 102. Accordingly, two handrail drives 2 are required to drive the two rotating handrails 3.
  • FIG. 2 schematically in the side view designed as a moving walk 110 conveyor system 110, which also has a balustrade 112 with Balustradensockel 119, a handrail 3, a supporting structure 116, and two deflection 117, 118.
  • a moving walk 110 conveyor system 110 which also has a balustrade 112 with Balustradensockel 119, a handrail 3, a supporting structure 116, and two deflection 117, 118.
  • between the deflection areas 117, 18 of the moving walk 110 is not a step band, but a pallet strip 115 with a plurality of pallets 114 arranged circumferentially.
  • the moving walk 110 connects for example a third floor E3 with a fourth floor E4.
  • the handrail 3 and the handrail drive 2 of the moving walkway 110 correspond to the handrail 3 and the handrail drive 2 of the escalator 100 of FIG. 1 why the same reference numerals are used. Even with a moving walk 110 usually two balustrades 112 are used with handrails 3, which extend to both sides of the pallet strip 115.
  • Fig. 3 shows the handrail drive 2 from the Figures 1 and 2 and a part of the handrail 3 in an excerpt, schematic sectional view according to an embodiment of the invention.
  • the handrail drive 2 can be manufactured and distributed independently of the other components of the conveyor system.
  • the handrail drive 2 according to the invention is preferably used in conveyor systems or transport devices which are designed as escalators 100 or moving walk 110.
  • the handrail drive 2 has a drive device 4 and a counter-pressure device 5.
  • a modified embodiment of the handrail drive 2 for example, also have a further counter-pressure device 5, which is designed according to the counter-pressure device 5.
  • the conveyor system 100, 110 may also have a plurality of handrail drives 2 in order, for example, to drive a plurality of handrails 3. In particular, viewed in the running direction, left and right of the footprint for persons and / or objects of the conveyor system 100, 110 provided handrails 3 can be driven.
  • the drive device 4 has a drive wheel 6, a tensioning wheel 7 and a drive belt 8.
  • the drive belt 8 is guided around the drive wheel 6 and the tensioning wheel 7.
  • the drive wheel 6 and the tensioning wheel 7 at their running surfaces 9, 10 each have a ring gear.
  • the drive belt 8 is designed as a toothed belt 8.
  • a poly-V belt could be used as a drive belt 8.
  • the tensioning wheel 7 is acted upon by an adjustable tensioning device 15, which comprises a belt tensioning spring 16, away from the drive wheel 6.
  • an adjustable tensioning device 15 which comprises a belt tensioning spring 16, away from the drive wheel 6.
  • the drive device 4 also has a plurality of contact pressure rollers 17 to 22.
  • the running surfaces 17 'to 22' of the contact pressure rollers 17 to 22 each have a toothed rim 17 'to 22'. With the sprockets 17 'to 22' engage the contact pressure rollers 17 to 22 in the teeth of the drive belt (toothed belt) 8 a.
  • the contact pressure rollers 17 to 20 are mounted on stationary axes 23 to 26 within the drive device 4.
  • the contact pressure rollers 21, 22 are mounted on movable axes 27, 28.
  • the handrail 3 for example, run in a running direction 29.
  • Another, possible running direction 30 is opposite to the direction 29.
  • the contact pressure rollers 17 to 22 also have a tooth profile.
  • the movable axes 27, 28 are movable within the mechanically provided limits in and counter to the direction 31, which is perpendicular to the running direction 29.
  • the contact pressure rollers 21, 22 are preferably urged in the direction 31 against the drive belt 8.
  • the counter-pressure device 5 has counter-pressure rollers 32 to 39.
  • the counter-pressure rollers 32 to 39 have running surfaces 32 'to 39', which in this embodiment are designed as smooth running surfaces 32 'to 39'. While an inner side 40 of the handrail 3 faces the contact pressure rollers 17 to 22 and the drive wheel 6 and the tensioning wheel 7, an upper side 41 of the handrail 3 faces the counter-pressure rollers 32 to 39. However, the contact pressure rollers 17 to 22 and the drive wheel 6 and the tensioning wheel 7 are not directly on the inside 40 of the handrail 3 at.
  • the drive belt 8 is partially directly to the inside 40 of the handrail 3 at. Thus, the contact pressure rollers 17 to 22 and the drive wheel 6 and the tensioning wheel 7 act on the drive belt 8 on the handrail 3 a. By means of the drive belt 8 can thus be transmitted to the handrail 3, the driving force in the selected direction 29, 30.
  • the counter-pressure rollers 32 to 39 are in this embodiment, with their running surfaces 32 'to 39' directly to the top 41 of the handrail 3 at.
  • the handrail 3 is acted upon by the counter-pressure rollers 32 to 39 against the drive belt 8 with a pressing force, which is caused by a tension spring 42.
  • the pressing force 45 preferably acts counter to the direction 31 and thus perpendicular to the running direction 29 of the handrail third
  • the tension spring 42 of the counter-pressure device 5 is arranged parallel to the running direction 29 in this exemplary embodiment.
  • the at least one tension spring 42 is arranged at least approximately parallel to the running direction 29. This means that a direction of action 43 of the tension spring 42, along which also the Spring force 44 of the tension spring 42 acts, is oriented parallel to the direction 29.
  • the parallel orientation is to be understood here in relation to the relevant central longitudinal axes and includes a so-called antiparallel orientation.
  • the drive belt 8 of the drive means 4 and the counter-pressure rollers 32 to 39 are arranged to each other so that the handrail 3 between the drive belt 8 and the counter-pressure rollers 32 to 39 in the direction 29 can be guided.
  • the handrail is thus acted upon by the counter-pressure rollers 32 to 39 against the drive belt 8 with the pressing force 45.
  • the pressing force 45 in turn is caused by the tension spring 42, that is, the spring force 44 of the tension spring 42.
  • the counter-pressure rollers 32 to 39 are in this case at least partially disposed in an extension 46 of the tension spring 42.
  • the boundaries 47, 48 of this extension 46 are here in the Fig. 3 illustrated by broken lines 47, 48.
  • the boundary 47 here represents the upper limit 47 with respect to the direction of the pressing force 45, while the limit 48 represents the lower limit in this respect.
  • a height 50 of the counter-pressure device 5 can be optimized, that is, as small as possible. Accordingly, the height 51 of the handrail drive 2, which is composed of the height 50 of the counter-pressure device 5, a height 52 of the drive device 4, a height 53 of the handrail 3 and optionally structurally required additional heights 54, 55, are reduced.
  • a vertical dimension 56 of the tension spring 42 has no influence on the overall height 51 of the handrail drive 2. Because the dimension 56 of the tension spring 42 is completely within the height 50 of the counter-pressure device 5. The dimension 56 is determined by the distance between the upper limit 47 and the lower limit 48. In this embodiment, the dimension 56 is equal to the outer diameter of the tension spring 42.
  • the tension spring 42 is not necessarily designed as a helical spring, so that the dimension 56 then correspondingly from the distance between the upper limit 47 and the lower limit 48 of the extension 46 results.
  • the term of the tension spring 42 also includes a package of a plurality of spiral springs, which in a direction 57 (FIG. Fig. 5 ), which is both perpendicular to the running direction 29 and perpendicular to the direction 31, are arranged side by side.
  • the tension spring 42 is also a package Be disc springs.
  • two or more coil springs serving as a tension spring 42 may be arranged in a horizontal plane parallel to each other without increasing the vertical dimension 56.
  • the counter-pressure rollers 32 to 39 are arranged only partially in the extension 46 of the tension spring 42. This is illustrated in this embodiment in that the counter-pressure rollers 32 to 39 to the handrail 3 out (in the FIG. 3 so up) beyond the upper limit 47 protrude and in this case even from the handrail 3 away (in the FIG. 3 so down) beyond the lower limit 48 protrude.
  • the handrail drive 2 on a support 58 on which the drive means 4 and the counter-pressure device 5 are attached.
  • a mounting bracket 59 of the counter-pressure device 5 is firmly connected to the carrier 58 and the support plate 58.
  • the handrail drive 2 of the conveyor system 100, 110 is described below with reference to the FIG. 4 and the FIG. 5 further described. For the sake of clarity are in the FIGS. 4 and 5 only the most important reference signs are registered.
  • FIG. 4 shows the in the FIG. 3 illustrated handrail drive 2 in an excerpt, schematic representation according to the embodiment of the invention.
  • FIG. 5 shows the counter-pressure device 5 of the handrail drive 2 according to the embodiment of the invention in a schematic, spatial representation.
  • the counter-pressure device 5 has a tension spring bearing 60, which is firmly connected to the mounting bracket 59. Since the mounting bracket 59 is fixedly connected to the carrier 58, thus the tension spring bearing 60 is stationary with respect to the carrier 58 is arranged.
  • the counter-pressure device 5 has a bearing body 61, the bearing plates 62, 63 (FIG. Fig. 3 ) for supporting axles 72 to 79.
  • the counter-pressure device 5 on a slider 64 which is formed in this embodiment by a sliding plate 64.
  • the slider 64 may be formed in a correspondingly modified embodiment but for example by slide rails.
  • a slide 65 is formed on the sliding plate 64. There the sliding plate 64 is fixedly connected to the mounting bracket 59, the slide 65 is stationary with respect to the carrier 58 is positioned.
  • the counter-pressure device 5 also has a guide 66 (FIG. Fig. 3 ), which is connected by means of the sliding plate 64 and the mounting bracket 59 with the carrier 58 and thus with the drive means 4.
  • the bearing body 61 has a guide pin 67 which is connected on the one hand to the bearing plate 62 and on the other hand to the bearing plate 63.
  • the guide pin 67 is guided in the guide 66.
  • About the guide pin 67 of the bearing body 61 is guided at this point relative to the drive means 4.
  • the guide is at least approximately perpendicular to the running direction 29. In operation, the direction of the pressing force 45 along the guide of the guide pin 67 results in the guide 66th
  • the counter-pressure rollers 32 to 39 are mounted on axles 72 to 79, which are each connected on the one hand to the bearing plate 62 and on the other hand to the bearing plate 63. As a result, the counter-pressure rollers 32 to 39 are mounted in the bearing body 61. The counter-pressure rollers 32 to 39 are in this case mounted one behind the other in the extension 46 of the tension spring 42 on the bearing body 61.
  • the axis 72 to 79 may be referred to as the first axis and the axis 79 as the second axis. Since in this embodiment more than two axes 72 to 79 are provided, on which the counter-pressure rollers 32 to 39 are mounted, the axes 73 to 78 may be referred to as further axes.
  • the first axis 72 and the second axis 79 are provided fixedly to the bearing body 61.
  • the counter-pressure roller 32 and on the second axis 79, the counter-pressure roller 39 are mounted on the first axis 72.
  • the counter-pressure roller 32 is in this case associated with the tensioning wheel 7.
  • the counter-pressure roller 39 is assigned to the drive wheel 6.
  • the first axis 72 can also be integrated as an additional axis in the bearing body 61, on the no Counter-pressure roller is arranged.
  • the second axis 79 may be integrated as an additional axis in the bearing body 61, on which no counter-pressure roller is arranged.
  • the embodiment described with reference to the exemplary embodiment represents a preferred special case in that the counter-pressure rollers 32, 39 are arranged on the first axis 72 and on the second axis 79. In order to realize the function of the first axis 72 and the second axis 79 described in more detail below, no additional axes are required, which reduces the space requirement for the counter-pressure device 5.
  • the counter-pressure device 5 of the handrail drive 2 has a deflection device 80.
  • the deflection device 80 has Gleit Resultss Mon 81 to 83, connecting rods 84 to 87 and other components.
  • Gleit Resultss Mon 81 to 83 the connecting rods 84 to 87 and other components.
  • FIG. 3 and 5 the sliding guide shoes 81 to 83 and the connecting rods 84 to 87.
  • the deflecting device 80 is mounted on the sliding track 65 via its sliding shoes 81 to 83.
  • a mobility of the deflecting device 80 along the direction of action 43 is made possible.
  • the direction of action 43 is in this case oriented parallel to the slideway 65.
  • the tension spring bearing 60 is in this case stationary to the slide 65.
  • the tension spring 42 thus has the function of pulling the deflection device 80 toward the tension spring bearing 60.
  • the tension spring 42 is connected in a suitable manner at least indirectly to the deflection device 80, which in this embodiment takes place, inter alia, via a rod 88.
  • the deflection device 80 serves for deflecting the spring force 44 of the tension spring 42 into the pressing force 45 of the counter-pressure rollers 32 to 39.
  • the deflection device 80 is designed as a mechanical deflection device 80.
  • the deflection device 80 has a first axle guide 90 with a guide track 91.
  • the first axle guide 90 is configured in the Gleit Resultssschuh 81 in this embodiment.
  • the first axle guide 90 is designed as a double-sided axle guide 90, which guides the first axis 72 at its two ends. The first axle guide 90 thereby guides the first axle 72 on the one hand in the vicinity of the bearing plate 62 and on the other hand in the vicinity of the bearing plate 63 of the bearing body 61.
  • the guideway 91 is thereby formed, as it were, by two surface elements lying in a guide plane 92.
  • the guide plane 92 and the action direction 43 include a predetermined deflection angle 93.
  • the characteristic predetermined deflection angle 93 defines that, irrespective of the position of the axis 72 within the axle guide 90, in the axle guide 90 or its guide plane 92, there is always a pitch that converts the spring force 44.
  • the deflection angle 93 is thus greater than 0 °.
  • the deflection angle 93 is an acute deflection angle 93, that is, less than 90 °.
  • the deflection angle 93 is preferably selected from a range of 5 ° to 45 °.
  • the deflection angle 93 can be selected from a range of 10 ° to 30 °. In particular, the deflection angle 93 can be selected from a range of 15 ° to 25 °. Specifically, the deflection angle 93 may be about 17 ° to 20 °.
  • the spring force 44 Due to the loading of the deflection 80 by the tension spring 42 acts between the first axis 72 and the guide track 91 of the first axle guide 90, the spring force 44 along the direction of action 43. Since the bearing body 61 with the bearing plates 62, 63 by the guide pin 67 and the guide 66th along this direction of action 43 has no degree of freedom, the spring force 44 is deflected in the pressure force 45 oriented perpendicular thereto in this embodiment. The mechanical deflection 80 thus allows the deflection of the spring force 44 of the tension spring 42 in the pressing force 45. The size relationship arises here neglecting friction effects and the like from the force parallelogram at the opposite direction of action 43 with the deflection angle 93 inclined track 91.
  • the guide 66 is rigidly connected via the carrier 59 to the tension spring bearing 60, on which the tension spring 42 is supported, the spring force 44 of the tension spring 42 acting on the bearing body 61 via the deflection device 80.
  • the sliding guide shoe 82 has a second axle guide 94 with a guide track 91.
  • the guide track 91 formed by two patches lies here in a guide plane 95.
  • the guide plane 95 includes with the direction of action 43 the same deflection angle 93, which also includes the guide plane 92 with the direction of action 43.
  • the Deflection of the spring force 44 of the tension spring 42 in the pressing force 45 thus both the first axle guide 90 and the second axle guide 94.
  • the operation and design of the deflection at the second axle guide 42 corresponds to that at the first axle guide 90, whereby a repeating Description is unnecessary.
  • further axes which are integrated into the bearing body 61, may be mounted in further axle guides 90, wherein in turn the same deflection angle 93 is provided. Further, the deflection may optionally also take place on a single axis guide or as shown in the present embodiment, also in the region of the guide pin 67 and the guide 66th
  • the counter-pressure roller 32 which is mounted on the first axis 72, the closest to the tension spring 42 and the tension spring bearing 60 arranged counter-pressure roller 32.
  • the counter-pressure roller 39 which is mounted on the second axis 79, the furthest In this way, the stability of the arrangement of the bearing body 61 in the deflection 80 can be improved by the tension spring 42 and the tension spring bearing 60 remotely located counter pressure roller 39. For example, thereby tilting and associated jamming or wedging can be avoided.
  • the counter-pressure rollers 32 to 39 are pressed with the pressing force 45 via the handrail 3 against the drive belt 8. Since the drive wheel 6, the tensioning wheel 7 and the contact pressure rollers 17 to 20 are not movably mounted in the direction of the pressing force 45, thus sets a balance of power when the handrail 3 at least largely rectilinearly between the drive device 4 and the Counter-pressure device 5 in the running direction 29 runs. The movement of the deflector 80 on the slide 65 of the slide plate 64 is thereby limited.
  • FIG. 6 schematically shows in side view a handrail drive 202 with two counter-pressure devices 205 and 206, which are arranged mirror-symmetrically to a mirror plane S.
  • the mirror plane S extends orthogonally to the running direction 29, 30 of the handrail 3 and is arranged approximately centrally of the drive device 4.
  • the counter-pressure rollers 32 to 39 are divided according to the two counter-pressure devices 205, 206, then the counter-pressure device 205 and the other, mirror-image counter-pressure device 206 can be assigned to a single drive device 4.
  • a further drive device 4 is provided.
  • the conveyor system 100, 110 may have per handrail 3 to be driven also two mirror-image handrail drives 2, which are arranged, for example, at the two ends of the traveling floor space for persons and / or objects or in front of the balustrade end curves, on which the handrail 3 is also deflected becomes.
  • the two tension springs are also replaced by a central spring, which is between the two Counter-pressure devices 205, 206 is arranged.
  • the central spring may be a tension spring or a compression spring. This arrangement also eliminates the two tension spring bearings.
  • the handrail drive 2 according to the invention can be used both in an escalator and in a moving walk.

Landscapes

  • Escalators And Moving Walkways (AREA)

Claims (15)

  1. Entraînement de main courante (2, 202) pour entraîner une main courante (3) d'une installation de transport (100, 110), lequel entraînement de main courante (2, 202) comporte au moins un dispositif d'entraînement (4) et au moins un dispositif de contre-pression (5, 205, 206), le dispositif de contre-pression (5, 205, 206) contenant au moins un ressort de tension (42) et au moins un galet de contre-pression (32 à 39), et la main courante (3) étant apte à être guidée entre le dispositif d'entraînement (4) et le ou les galets de contre-pression (32-39) à peu près dans un sens de roulement linéaire (29, 30) et étant apte à être contrainte par le ou les galets de contre-pression (32 à 39) contre le dispositif d'entraînement (4) avec une force de pression (45) provoquée par le ressort de tension (42), le ressort de tension (42) étant disposé à peu près parallèlement au sens de roulement (29, 30), et le ou les galets de contre-pression (32 à 39) étant disposés au moins en partie dans un prolongement (46) du ressort de tenson (42), caractérisé en ce que le dispositif d'entraînement (4) comporte au moins une courroie d'entraînement entraînée (8), et ladite courroie d'entraînement (8) et le ou les galets de contre-pression (32 à 39) sont disposés l'une par rapport aux autres de telle sorte que la main courante (3) soit apte à être guidée entre la courroie d'entraînement (8) et le ou les galets de contre-pression (32 à 39) et soit apte à être contrainte par le ou les galets de contre-pression (32 à 39) contre la courroie d'entraînement (8) avec la force de pression (45).
  2. Entraînement de main courante (2, 202) selon la revendication 1, ledit entraînement de main courante (2, 202) comportant un dispositif de déviation mécanique (80) à l'aide duquel la force de ressort (44) du ressort de tension (42) est apte à être déviée en force de pression (45) du ou des galets de contre-pression (32 à 39).
  3. Entraînement de main courante (2, 202) selon la revendication 1 ou 2, dans lequel le dispositif d'entraînement (4) comporte au moins une poulie d'entraînement (6), au moins une poulie de tension (7) et plusieurs galets presseurs (17 à 22), et la courroie d'entraînement (8) est entraînée par la poulie d'entraînement (6), le dispositif de contre-pression (5, 205, 206) comportant plusieurs galets de contre-pression (32 à 39), et les galets de contre-pression (32 à 39) du dispositif de contre-pression (5, 205, 206) et la poulie d'entraînement (6), la poulie de tension (7) et les galets presseurs (17 à 22) du dispositif d'entraînement (4) étant associés respectivement par paires.
  4. Entraînement de main courante (2, 202) selon la revendication 3, dans lequel les galets de contre-pression (32 à 39) sont disposés les uns derrière les autres dans le prolongement (46) du ressort de tension (42).
  5. Entraînement de main courante (2, 202) selon l'une des revendications 1 à 4, dans lequel le dispositif de contre-pression (5, 205, 206) comporte un corps d'appui (61) contre lequel le ou les galets de contre-pression (32 à 39) sont en appui.
  6. Entraînement de main courante (2, 202) selon la revendication 5, cet entraînement de main courante (2, 202) comportant un guide (66) qui est relié au dispositif d'entraînement (4), et le corps d'appui (61) est guidé par rapport au dispositif d'entraînement (4) à l'aide du guide (66), en au moins un point (67), à peu près perpendiculairement au sens de roulement (29, 30).
  7. Entraînement de main courante (2, 202) selon la revendication 6, dans lequel le guide (66) est relié rigidement à un appui de ressort de tension (60) contre lequel le ressort de tension (42) est en appui, et la force (44) du ressort de tension (42) contraint le corps d'appui (61) par l'intermédiaire du dispositif de déviation (80).
  8. Entraînement de main courante (2, 202) selon la revendication 7, dans lequel au moins un premier axe (72) est prévu de manière stationnaire sur le corps d'appui (61), et le dispositif de déviation (80) comporte au moins un premier guide d'axe (90) dans lequel le premier axe (72) est guidé, et le premier guide d'axe (90) guide le premier axe (72) avec un premier angle de déviation défini (93) par rapport au sens d'action (43) de la force (44) du ressort de tension (42).
  9. Entraînement de main courante (2, 202) selon la revendication 8, dans lequel au moins un galet de contre-pression (32) est monté sur le premier axe (72).
  10. Entraînement de main courante (2, 202) selon la revendication 9, dans lequel le galet de contre-pression (32) qui est monté sur le premier axe (72) est le galet de contre-pression (32) qui est le plus proche du ressort de tension (42).
  11. Entraînement de main courante (2, 202) selon l'une des revendications 8 à 10, dans lequel un second axe (79) est prévu de manière stationnaire sur le corps d'appui (61), le dispositif de déviation (80) comporte au moins un second guide d'axe (94) dans lequel le second axe (79) est guidé, et le second guide d'axe (94) guide le second axe (79) avec l'angle de déviation défini (93) par rapport au sens d'action (43) de la force (44) du ressort de tension (42).
  12. Entraînement de main courante (2, 202) selon l'une des revendications 1 à 11, dans lequel le dispositif de déviation (80) comporte au moins un coulisseau (81 à 83), le dispositif de contre-pression (5, 205, 206) comporte une glissière (65), le dispositif de déviation (80) est monté sur la glissière (65) par l'intermédiaire du ou des coulisseaux (81 à 83), et un appui de ressort de tension (60) contre lequel le ressort de tension (42) est en appui est disposé de manière stationnaire par rapport à la glissière (65).
  13. Entraînement de main courante (2, 202) selon l'une des revendications 1 à 12, ledit entraînement comportant deux dispositifs de contre-pression (205, 206) qui sont disposés en miroir par rapport à un plan de symétrie (S), lequel plan de symétrie (S) s'étend perpendiculairement au sens de roulement (29, 30) de la main courante (3) et est disposé à peu près au centre du dispositif d'entraînement (4).
  14. Installation de transport (100, 110) qui est conçue comme un escalier roulant (100) ou un trottoir roulant (110), avec au moins une main courante mobile (3) et au moins un entraînement de main courante (2, 202) selon l'une des revendications 1 à 13 qui sert à entraîner la main courante (3).
  15. Procédé pour moderniser une installation de transport (100, 110) existante, caractérisé en ce qu'au moins un entraînement de main courante de l'installation de transport (100, 110) est remplacé par au moins un entraînement de main courante (2, 202) selon l'une des revendications 1 à 13.
EP14799744.9A 2013-11-27 2014-11-14 Entraînement de main courante pour un escalier ou un trottoir roulant Not-in-force EP3074335B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP14799744.9A EP3074335B1 (fr) 2013-11-27 2014-11-14 Entraînement de main courante pour un escalier ou un trottoir roulant

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP13194551 2013-11-27
PCT/EP2014/074631 WO2015078709A1 (fr) 2013-11-27 2014-11-14 Mécanisme d'entraînement de main courante pour un escalier mécanique ou un trottoir roulant
EP14799744.9A EP3074335B1 (fr) 2013-11-27 2014-11-14 Entraînement de main courante pour un escalier ou un trottoir roulant

Publications (2)

Publication Number Publication Date
EP3074335A1 EP3074335A1 (fr) 2016-10-05
EP3074335B1 true EP3074335B1 (fr) 2018-01-03

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ID=49709494

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EP14799744.9A Not-in-force EP3074335B1 (fr) 2013-11-27 2014-11-14 Entraînement de main courante pour un escalier ou un trottoir roulant

Country Status (5)

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US (1) US9745173B2 (fr)
EP (1) EP3074335B1 (fr)
CN (1) CN105764832B (fr)
ES (1) ES2657419T3 (fr)
WO (1) WO2015078709A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3224189B1 (fr) * 2014-11-28 2018-09-26 Inventio AG Entraînement de main courante pour un escalier ou un trottoir roulant
US10674285B2 (en) 2017-08-25 2020-06-02 Starkey Laboratories, Inc. Cognitive benefit measure related to hearing-assistance device use
CN107651549B (zh) * 2017-10-25 2023-12-15 广州广日电梯工业有限公司 一种自动扶梯的模块式扶手龙头
EP3511284B1 (fr) 2018-01-10 2021-09-15 Otis Elevator Company Trottoir roulant

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4875568A (en) * 1989-01-05 1989-10-24 Otis Elevator Company Escalator handrail drive
US5117960A (en) * 1991-08-15 1992-06-02 Otis Elevator Company Linear belt handrail drive
US5341909A (en) * 1993-08-30 1994-08-30 Otis Elevator Company Linear wheel escalator handrail drive
US5307920A (en) * 1993-09-14 1994-05-03 Otis Elevator Company Moving handrail drive
US7954619B2 (en) * 2007-06-01 2011-06-07 Kone Corporation Load sharing handrail drive apparatus
CN201777766U (zh) * 2010-05-19 2011-03-30 蒂森克虏伯扶梯(中国)有限公司 一种扶手带驱动装置

Also Published As

Publication number Publication date
WO2015078709A1 (fr) 2015-06-04
CN105764832B (zh) 2017-09-22
ES2657419T3 (es) 2018-03-05
US9745173B2 (en) 2017-08-29
CN105764832A (zh) 2016-07-13
EP3074335A1 (fr) 2016-10-05
US20170001843A1 (en) 2017-01-05

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